WO2006042286A1 - Cooling assembly - Google Patents
Cooling assembly Download PDFInfo
- Publication number
- WO2006042286A1 WO2006042286A1 PCT/US2005/036721 US2005036721W WO2006042286A1 WO 2006042286 A1 WO2006042286 A1 WO 2006042286A1 US 2005036721 W US2005036721 W US 2005036721W WO 2006042286 A1 WO2006042286 A1 WO 2006042286A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- air
- cooling chamber
- cooling
- plenum
- sump
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0035—Indoor units, e.g. fan coil units characterised by introduction of outside air to the room
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/005—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted on the floor; standing on the floor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0083—Indoor units, e.g. fan coil units with dehumidification means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0087—Indoor units, e.g. fan coil units with humidification means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/0035—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using evaporation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
- F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/54—Free-cooling systems
Definitions
- the present invention relates in general to low power air conditioning systems, and, in particular, to a low power air conditioning system employing a tube and shell heat exchanger for use in arid conditions and to a combination direct/indirect evaporative cooler with refrigerated sump water for use in other environments.
- the present invention provides air conditioning for structures that are located in arid, high temperature environments, such as deserts. Such environmental control is essential to enjoying a good quality of life, and, in some instances, is essential to supporting life. This is true for both humans and livestock.
- Some dwellings and particularly buildings in which livestock may be kept are not well sealed or insulated so there is little impediment to the interiors of such structures reaching thermal equilibrium with the exterior environment.
- such structures are not provided with air conditioning systems because of the cost of operating them and the general ineffectiveness of air conditioning systems in such structures.
- Most air conditioning systems operate on electricity, and electricity is not always available, or is not available at a reasonable price where the structures are located. It would be greatly beneficial to both human beings and livestock if an effective, simple, self-contained air conditioning system could be provided for desert environments that would operate inexpensively in unsealed structures.
- evaporative cooling of buildings has been accomplished by injecting a fog or mist of water into a moving stream of air. See, for example, Atkins, U.S. 5,146,762.
- One problem with this system is that it causes excess humidity within the building resulting in algae and bacteria problems.
- Atkins proposes to minimize some of these problems by placing exhaust fans at one end of a building widely spaced from fogger nozzles at the opposite end of the building. The disclosed rate of water consumption is very high. In excess of 95 percent of the water supplied to the fogger nozzles is consumed. Atkins' evaporative cooling system is said to produce a temperature drop of approximately 20 degrees.
- Urch U.S. 6,434,963 discloses an air cooler with two airflow paths, namely, an inlet path for outside air and an outlet path for stale air.
- a heat exchanger pre-cools the fresh air with heat extracted from the stale air, and further cooling is achieved by means of an evaporative cooler that spans the two air flow paths.
- the air conditioning assembly comprises a shell and tube heat exchanger wherein ambient air is forced through both sides and discharged approximately together into the interior of the structure that is to be cooled.
- the air streams from the two sides can be combined into one combined stream before being discharged into the interior of the structure, or they may be discharged separately into the structure.
- This heat exchanger is particularly suited for use in the high heat and low humidity conditions that are typically found during the summer months in deserts.
- the air conditioning assembly is particularly effective in situations where the temperature is above approximately 80 degrees Fahrenheit, and the relative humidity is below approximately 40 percent, and, preferably, below approximately 35 percent.
- the assembly is suitably operable even in situations where the structure to be air conditioned is not tightly sealed, that is where there may be openings through the structure that are substantially unobstructed to airflow having as much as, for example, six square inches to a square foot or two of area.
- Barns, tents, temporary structures and the like are provided with an efficient, reliable, economical, simple, and effective air conditioning system according to the present invention.
- the air conditioning system according to the present invention does not require an elaborate or expensive installation for its functioning. It can be easily transported to and set up inside of a temporary structure such as, for example, a tent.
- the shell side of the heat exchanger is preferably wet with a shower or weep of a liquid such as water, and the air flow is turbulent through the shell side.
- the stream of flowing air is directed from the shell side to an outlet.
- the air flowing through the tube side is cooled by contact with the walls of the tubes, and is discharged to an outlet.
- the air streams from the shell and tube sides are combined and discharged into the interior of the structure that is to be cooled. These air streams can be combined after discharge into the interior of the structure, if desired.
- the intake and discharge of the air streams are all within the interior of the structure.
- the present invention comprises a direct/indirect evaporative cooler with refrigerated chilled sump water.
- the cooler is preferably designed as a stacked arrangement.
- a refrigeration compressor and storage batteries occupy a top section of the design and rest on a top shelf.
- the top shelf forms the top wall of an exhaust air plenum.
- a cold water sump and an intake air plenum occupy the bottom floor of the cooling chamber.
- the bottom floor of the cooling chamber also comprises the top wall of an intake plenum which houses an intake fan.
- the intake fan draws air upwardly through a plurality of riser tubes which connect the intake plenum with the exhaust plenum and which pass through the cooling chamber.
- Water in the cold water sump is refrigerated by the refrigeration compressor located in the top section of the design.
- Cold water from the cold water sump is introduced into the evaporative cooling chamber through a distribution header.
- the cold water saturates an evaporative media which surrounds or otherwise contacts the riser tubes in the cooling chamber.
- Air is introduced into the cooling chamber by means of oppositely arranged fans mounted on sidewalls of the cooling chamber which create a turbulent airflow in the cooling chamber and which enhance the evaporative cooling process. Cooled air from the cooling chamber can be discharged through a suitable duct to the interior of the structure to be cooled.
- Air is also being drawn into the intake plenum by the intake fan, which air flow is forced upwardly through the riser tubes in the cooling chamber.
- the riser tubes pass though the cold water sump and also contact the evaporative media in the cooling chamber, whereby the outside of the tubes are cooled.
- the air within the tubes is cooled by conduction through the tubes.
- This relatively drier air can be directed through a suitable duct to the interior of the structure to be cooled and can be combined with the more moist, cooled air from the cooling chamber, if desired.
- air is being cooled using two simultaneous processes. Air is cooled by direct contact with water in the evaporative cooling chamber, raising the absolute humidity of the air cooled in this manner. Additional air is also being cooled by conductive heat transfer within the riser tubes. If desired, the two airflows can be combined into a discharge duct so that the discharged air consists of a mixture of relatively humid air from the evaporative process and air with near ambient humidity.
- the cold water sump at the bottom of the cooling chamber serves as a cooling mass, as well as a water storage sump.
- the water in the sump is refrigerated to near freezing by means of a low temperature compressor similar to that used on an ice machine.
- the compressor can be AC or DC operated.
- the electric fans used in the intake plenum and on the cooling chamber are preferably DC fans which can be driven by solar cells or storage batteries.
- an additional refrigeration manifold may be located inside the wet chamber in the vicinity of the discharge outlet from the wet chamber.
- the additional refrigeration manifold can be supplied with refrigerant from the existing mechanical refrigeration system used to chill the sump water in the wet chamber.
- Pump down valves control the flow of refrigerant to the additional manifold so that the manifold is only cooled when the oppositely arranged fans mounted on the sidewalls of the wet chamber are running.
- the air entering the wet chamber can be ducted so that either outside air is being introduced, or so that room air from the lower dry chamber of the assembly is being introduced.
- the air conditioning assembly can be installed within a room having ceiling vents which are used to move static airto the attic space for subsequent discharge to the exterior of the structure being cooled.
- Figure 1 is a diagrammatic view of one embodiment of a tube and shell heat exchanger according to the present invention.
- Figure 2 is a cross-sectional view taken along line 2-2 In Fig. 1.
- Figure 3 is a diagrammatic cross-sectional view taken through the shell plenum of a further embodiment according to the present invention showing a liquid spray system.
- Figure 4 is a diagrammatic cross-sectional view taken through the shell plenum of a further embodiment according to the present invention showing the tubes fully enclosed in blankets.
- Figure 5 is a plan view of a structure in which a tube and shell heat exchanger air conditioning system according to the present invention has been installed.
- Figure 6 is a cross-sectional view of the heat exchanger of Fig. 5 taken through the shell plenum.
- Figure 7 is a chart of the temperature and relative humidity readings recorded in Tables 4 and 5 at locations 116 and 120 in Fig. 5.
- Figure 8 is a perspective view of another embodiment of the device of the invention which features combined direct/indirect evaporative cooling with refrigerated chilled sump water.
- Figure 9 is a rear view of the device of Fig. 8 with the rear wall removed for ease of illustration of the internal components of the device.
- Figure 10 is an isolated view of the cooling chamber and refrigeration manifold used in the device of Fig.'s 8 and 9.
- Figure 11 is a perspective view of the device of Fig.8 with the rear wall removed for ease of illustration of the internal components of the device.
- Figure 12 is a view of the top wall of the cooling chamber which also serves as a tube sheet for the riser tubes.
- Figure 13 is an isolated view of the cooling chamber of the device of Fig. 8.
- Figure 14 is a side view of the cooling chamber showing the location of the water distribution array.
- Figure 15 is an isolated view of the air intake plenum and air intake fan.
- Figure 16 is an isolated view of the refrigeration manifold used in the cold water sump of the device of Fig. 8.
- Figure 16A is a cross sectional view taken along lines 16A-16A in Fig. 16.
- Figure 16B is a simplified end view of the manifold of Fig. 8 showing the cross-over piping arrangement used to produce the interlayered flow pattern.
- Figure 17 is a simplified, schematic view of an auxiliary heat exchange unit which can be operated off the chilled water in the cold water sump of the device of the invention.
- Figure 18 is a cross-sectional view of a cable used to connect the auxiliary heat exchange unit of Fig. 17 with the main cooling assembly shown in Figs. 8-15.
- Figure 19 is a schematic view of the additional refrigeration manifold which is installed within the wet chamber of the high humidity version of the air conditioning system of the invention, along with the associated refrigeration circuit for the manifold.
- Figure 20 is a simplified, schematic view of the air flow through a structure utilizing an air conditioning system of the invention.
- Figure 21 is a schematic view of an alternate ducting arrangement for the air flow to the wet chamber of the device of the invention.
- a tube and shell heat exchanger which is particularly adapted for use as a low power air conditioning unit in high temperature, low humidity conditions with structures that are not hermetically sealed.
- the floor plan of such a structure is indicated generally at 64 in Fig. 5.
- Heat exchanger 10 is confined within external case 62.
- external case 62 is shown as rectangular, but other arcuate, spherical, or cylindrical forms are contemplated within the scope of the present invention.
- Air preferably internal air from near the ceiling of a structure that is to be cooled, is drawn into the tube side of the heat exchanger through inlet port 12 into intake plenum 14 of heat exchanger 10. Air is drawn into inlet port 12 by exhaust fan 46. Air is drawn from intake plenum 14 through heat exchange tubes 34 into exhaust plenum 18. Tube inlet ends 36 are sealingly mounted in inlet tube sheet 60, and tube outlet ends 38 are sealingly mounted in tube outlet sheet 32.
- Exhaust fan 46 expels the air from the tube side of the heat exchanger into tube side exhaust conduit 22.
- the shell side of heat exchanger 10 is in the form of a shell plenum 16 that surrounds heat exchange tubes 34 between inlet tube sheet 60 and outlet tube sheet 32.
- Heat exchange tubes 34 are shown for the purposes of clarity of illustration as being straight, but, as will be understood by those skilled in the art, other forms such as coiled or looped heat exchange tubes can be used.
- a body of liquid, preferably water, is disposed within the shell side of heat exchanger 10..
- the surface of the body of liquid is indicated at 50.
- the liquid generally occupies less than one-half, and preferably, less than one-quarter of the volume of the shell side of the heat exchanger.
- the bottom portion of the shell plenum 16 forms a liquid sump in which the liquid resides.
- At least one, and preferably at least two fans are position to force ambient internal air from within the structure into shell plenum 16 of heat exchanger 10.
- three such shell side input fans are indicated at 40 (first input fan), 42 (second input fan), and 44 (third input fan). These fans together generate substantial turbulence in the air on the shell side of heat exchanger 10. The air from shell plenum 16 is expelled from heat exchanger 10 through shell side exhaust conduit 20.
- the liquid in the sump within shell plenum 16 is sprayed over the heat exchange tubes 34.
- a spray system is illustrated in Fig. 1 , and consists of a pump feed line 26 that serves to convey liquid from the liquid sump on the shell side to liquid pump 24. Pump 24 supplies energy to the liquid and discharges it through pump discharge line 28 to spray head 30 where it is sprayed over the shell sides of heat exchange tubes 34.
- Spray head 30 is typically located at or near the top of the shell side plenum, although this is not necessary to the operation of the system. It is schematically illustrated here on the side of the shell side plenum for ease of illustration. The liquid runs and falls back down into the sump where it is recycled again.
- the liquid spray enhances the heat transfer between the heat exchange tubes 34 and the liquid, as well as rapidly increasing the humidity of the air in the shell plenum 16.
- the liquid level is automatically maintained at about a constant level by means of a conventional float actuated valve connected to a supply of liquid (not shown).
- Heat transfer between the liquid and the heat exchange tubes 34 is further enhanced by the provision of blanketing members, for example, tubular foam blankets 48 (Fig.4), or loose reticulated foam sheets 104 (Fig. 6) positioned in physical contact with the heat exchange tubes 34.
- blanketing members for example, tubular foam blankets 48 (Fig.4), or loose reticulated foam sheets 104 (Fig. 6) positioned in physical contact with the heat exchange tubes 34.
- the humidification of the air in shell plenum 16 is enhanced by the presence of blanketing members of some form.
- the blanketing members hold the liquid against the heat exchange tubes 34, and increase the surface area of the liquid within shell plenum 16.
- the blanketing members comprise inert reticulated material through which liquid and vapor phase liquids flow easily. Numerous such reticulated materials are known, including, for example, many natural and synthetic open pore foams, felts, battings, woven materials, and the like.
- blanketing elements Conventional commercial swamp cooler pads are generally suitable for use as the blanketing elements. Often such materials include bacteria stats, fungi stats, and the like.
- the blanketing materials can completely or partially enclose heat exchange tubes 34, as desired. Compare, for example, Figs. 4 and 6. For the sake of clarity of illustration, these blanketing members are not illustrated in Figs. 1 , 2, and 3, but they are preferably employed in some form.
- Various liquid spray systems can be employed. A particularly effective system is illustrated particularly in Fig. 3. Liquid from a suitable source such as, for example, the sump in shell plenum 16, is supplied under pressure to spray header 52 and distributed to spray header branches 56. Liquid is expelled in a shower from spray ports 54.
- spray header 52 is positioned at the normally upper end of shell plenum 16 adjacent to outlet tube sheet 32 so that liquid showers down over the heat exchange tubes 34 and any associated blanket material, and is acted upon by the turbulent airflow from the shell side fans 40, 42, and 44.
- the air exhausted from the tube side through exhaust conduit 22 is preferably mixed with the air exhausted from the shell side through exhaust conduit 20.
- the combined air streams are discharged to the ambient interior of the structure that is being cooled through combined exhaust conduit 58.
- An unfinished barn indicated generally at 64 has a rectangular shape about 30 feet wide and 50 feet long.
- barn 64 is oriented east to west along its long axis as indicated by the letters N, S, E, W, in Fig. 5.
- barn 64 has an uninsulated peaked metal roof, exposed 2 by 4 wooden stud walls, and a stucco exterior finish. The peak of the roof is about 10 feet from the floor, and the exterior walls are about 8 feet high.
- the interior volume of barn 64 is approximately 13,500 cubic feet.
- the exterior doors are not weather sealed and the total unsealed area around the exterior doors 66, 68, 70, 72, and 74 combined is from approximately 1 to 2 square feet.
- Stall partitions 82, 84, 86, and 88 are half height, and stall dividers 80 and 78 are full height extending to within approximately 6 inches of the roof.
- Interior gate 76 is a full height security screen door.
- the air conditioning system employed in barn 64 consists of tube and shell heat exchanger 10, combined exhaust conduit 58, air distribution chamber 92, air distribution branches 94 and 96, and air outlet heads 98 and 100.
- Input fans 42 and 44 supply ambient air from the interior of barn 64 to the shell plenum in heat exchanger 10.
- the air is typically drawn into the shell side of the heat exchanger from a level well below the level at which air is discharged at 98 and 100.
- Air is preferably drawn into the tube side of the heat exchanger from the hottest part of the structure adjacent to the uninsulated roof.
- Air exhausted from the tube side of heat exchanger 10 through tube side exhaust conduit 22 mixes with air exhausted from the shell side through conduit 20, and flows through combined exhaust conduit 58 to air distribution chamber 92.
- Air then splits and flows through each of air distribution branches 94 and 96 to respective air outlet heads 98 and 100.
- Air is drawn into the tube side of heat exchanger 10 through inlet port 12.
- Blanket material 104 (Fig. 6) in the form of conventional swamp cooler foam pads is in contact with tubes 34.
- a spray head of the general configuration shown in Fig. 3 positioned in the top of the shell plenum of heat exchanger 10. Preferably, approximat ⁇ ly the lower one-quarter of the shell plenum is filled with water.
- the rectangular exterior case of heat exchanger 10 is approximately 3 feet high by 2 feet by 2 feet, and it rests on the floor of barn 64.
- Input fans 42 and 44, mounted on opposed sides of the case, are 14 inches in diameter, run at 2,200 revolutions per minute, and operate on 12 volts of direct current. The rated amperage of these fans is 4 amps.
- the tube side exhaust fan 46 (Fig. 1) is a 12 inch, 12 volt, direct current, 4 amp fan. These fans are conventional automotive equipment, and they are typically used in association with conventional radiator cooling systems to pull air through the radiator of a liquid cooled internal combustion engine.
- the liquid pump 24 (Fig. 1) has a 12 volt, 7 amp, direct current motor, and a rated flow rate of 28 gallons per hour.
- the dimensions of the tube side intake plenum 14 are about 6 inches high by 24 inches by 24 inches.
- the dimensions of the tube side exhaust plenum 18 are about 6 inches by 24 inches by 24 inches.
- the dimensions of the shell side plenum 16 are about 24 by 24 by 24 inches.
- the heat exchange tubes 34 are straight sections of standard three- quarter inch cylindrical copper tubing having a length between tube sheets 32 and 60 of about 24 inches. There are 100 heat exchange tubes 34 arrayed in a generally regularly spaced rectangular pattern.
- the total surface area of the tubes 34 within shell plenum 16 is approximately 6,600 square inches.
- the intake port 12 for the tube side of the heat exchanger has a diameter of about 6 inches as do conduits 20 and 22.
- Intake port 12 opens upwardly and is positioned approximately 4 inches below the uninsulated metal roof of barn 64 so it is taking in approximately the hottest air within the interior of barn 64.
- Combined exhaust conduit 58 runs overhead, as do air distribution branches 94 and 96.
- the diameter of conduit 58 is about 8 inches, and conduit 58 is approximately 14 feet long.
- Each air distribution branch is approximately 10 feet long and 6 inches in diameter.
- the distribution box 92 is approximately 2 by 2 by 2 feet.
- the short leg of conduit 58 that runs into distribution box 92 is approximately 3 feet long.
- Air outlet heads 98 and 100 discharge downwardly at a height of approximately 9 feet above the floor.
- the pump and fans have, for example, direct current motors powered by 5 conventional 12 volt deep cycle lead acid secondary batteries connected in parallel, indicated generally at 106.
- the batteries are connected through a conventional charging circuit indicated generally 108 to 3 conventional 30 volt, 4 amp hour solar panels indicated generally at 110, 112, and 114.
- the solar panels are mounted on the south facing pitch of the roof of barn 64. No other power source is required for the full time daylight operation of the air conditioning system.
- a conventional AC converter could be used to charge the batteries off of regular 110 volt house current, or some other power from a commercial utility service. This is not necessary, and would add to the cost of operation while limiting the system to use only at locations where commercial utility service is available.
- the motors on the fans and pump could be replaced with conventional motors that would operate on power from a commercial utility service, but the costs of operation would be increased, and the flexibility of the system would be compromised.
- the level of water in the sump is preferably maintained at approximately 5 inches. At this level the sump contains approximately 1.67 cubic feet of water.
- the shell side plenum has a volume of approximately 8 cubic feet, so the water occupies approximately 21 percent of the volume of the shell, side plenum 16. This provides an adequate reserve of water to continue operations for more than a day.
- Other sump volumes can be used if desired, ranging from, for example, approximately 10 to 30 percent of the volume of the shell side plenum chamber 16.
- the sump need not be within the shell side plenum chamber.
- An external sump several times larger than the shell side plenum can be used if desired so as to provide for at least a week of unattended operation without replenishing the water supply. Less than a gallon of water is consumed during the course of the daylight hours in a typical summer day.
- Barn 64 is located in a desert area where the daytime temperatures typically exceed 100 degrees Fahrenheit for several months during the summer, the relative humidity is often below 20 percent, and the sun shines for most of the daylight hours. Without air conditioning, the temperature at mid-day within barn 64 usually exceeds the outside temperature by at least approximately 10 degrees Fahrenheit.
- the operation of the air conditioning system in barn 64 can be automated by providing a conventional thermostat (not shown) connected to the fans and pump circuits. Setting a thermostat at, for example, 74 degrees Fahrenheit, will activate the system early in the morning on a typical summer day, and keep it running well into the evening hours.
- a preferred air conditioning assembly according to the present invention is fully self contained. That is, the power supply for the fan and pump motors is at the same location as the rest of the system.
- the water supply on the shell side of the heat exchanger can be replenished automatically by a float actuated valve on a water line, or manually, as desired. Where no reliable water supply is available, the rate of water consumption is so low that manual replenishment at widely spaced intervals is practical.
- a low voltage (12 or 24 volts) battery system coupled with a conventional solar panel driven charging circuit is sufficient to power the system during the daylight hours.
- the convenience of using a conventional solar panel charged battery system, and the widespread availability of such inexpensive systems, makes practical the unattended air conditioning of a wide variety of structures. Even livestock barns, for example, can be reliably and inexpensively air conditioned according to the present invention. Dwellings occupied by humans can likewise be air conditioned, even where very limited funds are available to devote to this purpose, and the dwellings are poorly sealed and uninsulated.
- the battery system can also be charged by wind turbines in areas where reliable wind flows are available. Other alternative energy sources can be used, if desired.
- Combinations of solar panels, wind turbines and other forms of alternative energy are suitable for use in charging the battery system. Since alternative energy sources typically do not deliver a constant level of energy, and the motors employed in the system require a substantially constant energy source, batteries are preferably interposed between the energy source and the air conditioning system. Where an alternative energy source is capable of delivering a constant source of energy, the use of a battery system is optional.
- the air conditioning system according to the present invention was turned on in barn 64 at about 6:30 In the morning on a typical sunny summer day, and allowed to run all day.
- the inside temperature of barn 64 was measured at approximately location 102 (Fig. 5) approximately 4 feet above the ground, and the exterior temperature was measured in the shade under an open awning adjacent to the south side of barn 64 at approximately location 116.
- Location 116 is at a height of about 5 feet above the ground on a support for a 20 foot wide awning (not shown).
- the wooden awning is attached to the barn and extends outward from the level of the top of the wall of the barn 64 for about 20 feet.
- the wooden awning is completely open on three sides,
- the temperature at 116 is approximately what the temperature would be Inside of bam 64 without the air conditioning system. The temperatures observed were as shown In Table 1 below.
- the relative humidity remains substantially stable and constant throughout the day and throughout the interior of the structure.
- Temperature and relative humidity measurements were taken throughout a sunny day at various locations within and adjacent to barn 64. The readings were taken at the locations indicated by the reference numbers in Fig. 5 and were recorded in Table 4. The measurements at locations 118 and 120 were taken about 5 feet above the floor. Location 118 gives an indication of the effect of radiation from the exterior wall. Location 124 is on the north side of the barn 64 about 5 feet above the ground. The measurements were as follows:
- the last column in Table 5 reflects a drop in the voltage of the battery system during the hours of peak demand. This voltage drop is reflected in a decrease in the volume of air that the various fans are able to move through the system.
- temperature curve 120-5, Fig. 7 there is a small temperature rise (temperature curve 120-5, Fig. 7) that may be correlated with the reduced volume of air moving through the system between approximately 2 p.m. and 6 p.m.
- the system appears to be relatively insensitive to small changes in the volume of air flowing through the system.
- the voltage should be at least approximately 11 volts for optimum operation of the fan motors. Adding another one or two solar panels to the existing three panel array on the roof of barn 64 would provide enough capacity to hold this voltage during peak demand periods.
- the column headed "122 T" in Table 5 indicates the exterior temperature of the shell side of the heat exchanger.
- the water within the shell side is typically approximately 10 to 15 degrees Fahrenheit cooler than location 122. This affords the opportunity to provide some cooling to objects placed in heat exchange relationship with this water. If access is provided to the shell side, small objects can be cooled somewhat without the expenditure of significant additional amounts of energy. The shelf life of small amounts of heat sensitive food stuffs or medicines can be extended by placing them in heat exchanging relationship with this water. Suitable containers can be placed directly in the water on the shell side, or a cabinet accessible from the outside can be built into the shell side, or a stream of water circulated through, for example, cooling coils external to the shell side, or the like, can be utilized to effect the cooling of objects.
- the column headed "118 T” in Table 5 gives a rough indication of the heat that is being radiated into the interior of the structure by the exterior walls.
- the column headed “124 T” provides a rough indication of the effect of cooling the interior of barn 64 on the temperature of the exterior of the walls.
- Location 116 is far enough from the adjacent wall that there is very little if any influence on the indicated temperature by reason of the cooling of the interior of the barn 64.
- Comparison of columns 120, 98, and 100 indicates that the temperature is relatively uniform throughout the interior of barn 64.
- thermally insulating the case that encloses the heat exchanger improves the efficiency of the system by as much as 10 percent or more.
- the temperature of the body of water on the shell side tends to be reduced by the presence of the thermal insulation.
- the degree of thermal insulation is preferably such that the exterior temperature of the shell side of the heat exchanger (Table 5, column 122T) is at least 3, and preferably 5 degrees Fahrenheit warmer than the equivalent uninsulated metal exterior shell side temperature at an ambient air temperature of approximately 80 degrees Fahrenheit.
- Changing from a metal case (18 gauge steel) to a fiberglass (glass filament reinforced thermosetting resin) case with a thickness of approximately one- eighth inch reduces the temperature by approximately 5 degrees at about 80 degrees Fahrenheit ambient internal air temperature.
- the efficiency of the air conditioning system also increases. Numerous forms of insulation and methods of application are suitable for this purpose, as will be understood by those skilled in the art.
- the rate of water consumption in an air conditioning, system according to the present invention is very low.
- the rate of water consumption is no more than approximately 5 percent that of a conventional evaporative cooler (commonly described as a swamp cooler) operating under the same conditions.
- This low rate of water consumption is achieved even though the structure or other confined space is uninsulated, and is so unsealed that it is free to leak substantial volumes of air.
- the rate of water consumption of a heat exchanger according to the present invention is less than approximately 10 percent, and preferably less than approximately 5 percent that of a conventional direct evaporative cooler (in a conventional evaporative cooler a single stream of air passes through a moist environment and is cooled and humidified by the evaporation of water) operating under substantially the same conditions external to the cooling systems.
- substantially the same external conditions comprise about the same exterior conditions of temperature and relative humidity, and the same structure or other confined space with, for example, the same volume, shape, and insulation.
- the differences in the results from the operation of the cooling system of this invention as compared to the operation of a conventional evaporative cooler arises from the differences in the cooling systems, and not from the environment external to the coolers or the characteristics of the structure or other confined space. All of the variables, other than those inherent in the two cooling systems, are held constant for comparison purposes. That is, all of the external variables are held substantially constant. This low rate of water consumption is achieved while typically enjoying a humidifying efficiency (dry-bulb temperature drop across the heat exchanger divided by the maximum possible dry-bulb temperature drop as determined from a Psychometric chart) of from approximately 30 to 40 percent.
- the relative humidity within the interior of an air conditioned structure according to the first embodiment of the present invention is substantially below that which would be expected from a conventional evaporative cooler.
- Comparison of, for example, the data in columns "116 1/H" and "120 T/H” in Tables 4 and 5 reveals that when the exterior ambient temperature exceeds approximately 95 degrees Fahrenheit, and the exterior ambient relative humidity falls below approximately 25 percent, the relative humidity within the structure is only approximately twice (200 percent) that in the exterior environment. As the exterior relative humidity falls below approximately 20 percent, and the temperature exceeds approximately 100 degrees Fahrenheit, the interior relative humidity is generally greater than approximately twice that of the ambient exterior environment, but still less than approximately 2.3 times (230 percent) that of the ambient exterior environment.
- variable humidity embodiment of the invention which can be used in high temperature, low humidity environments such as that previously described, but which can also be used in higher humidity environments, including tropical or semi-tropical environments.
- an air conditioner 201 which is a combined direct/indirect evaporative cooler with refrigerated chilled sump water.
- the variable humidity device 201 shown in Fig. 8 has a number of common features with the low humidity device described with reference to Fig.'s 1-7.
- the air conditioner 201 is preferably designed as a stacked arrangement having atop section 203, a middle section 205 and a bottom section 207.
- a refrigeration compressor 209, an associated condenser unit 210, and a storage battery 211 (Fig. 9) occupy the top section 203 of the design and rest on a top shelf 213.
- the top shelf 213 forms the top wall of an exhaust air plenum 215 having an opposing wall 216.
- a forced-air evaporative cooling chamber (217 in Fig. 9) is located below the exhaust air plenum and occupies the middle section of the design.
- the cooling chamber comprises a shell plenum for the air conditioner and comprises about 65% of the total height of the unit in the particular embodiment illustrated in the drawings.
- a cold water sump 219 (indicated by dotted lines in Fig. 9) is located in the bottom of the cooling chamber.
- the bottom floor 223 of the cooling chamber 217 also comprises the top wall of an intake plenum 221 housing an intake fan 225.
- the intake fan 225 draws air upwardly through a plurality of riser tubes 227 which connect the intake plenum 221 with the exhaust plenum 215 and which pass through the cooling chamber 217.
- the bottom floor 223 of the cooling chamber has a plurality of openings 224 which form a lower tube sheet for the riser tubes 227.
- the opposing wall 216 has aligned openings (214 in Fig.'s 10 and 13) which form an upper tube sheet.
- the distribution header in Fig.9 is a series of PVC pipes which have downwardly directed perforations.
- the cold water which is sprayed downwardly from the distribution header saturates an evaporative media which surrounds or otherwise contacts the riser tubes 227 in the cooling chamber 217.
- the evaporative media is removed for ease of illustration in Fig.'s 9 and 11 but can comprise any of the media materials previously described with respect to the first embodiment of the invention.
- the evaporative media is supplied as generally rectangular pads which are suspended from a rack (241 in Fig. 14) on the roof of the cooing chamber so that the pads are spaced between and separate the various vertical riser tubes 227.
- Air is introduced into the cooling chamber by means of oppositely arranged fans 231 , 233.
- the fans 231 , 233 are mounted on louvers (235, 237 in Fig. 9) which can be manually adjusted to direct incoming and exhaust air from the cooling chamber 217 in a circular, vortex type flow path which creates a turbulent air flow in the cooling chamber 217 and which enhances the evaporative cooling process.
- the vortex effect created by the side louvers 235, 237 causes air moving through the cooling chamber 217 to have an increased residence time within the cooling chamber. This increases the cooling effect and also prevents water droplets from being blown directly out of the shell plenum.
- Cooled air from the cooling chamber can be discharged through a suitable grate (such as grate 239 in Figure 8) to the interior of the structure to be cooled or can be routed through suitable ducts to the desired regions of the interior of the structure being cooled.
- a suitable grate such as grate 239 in Figure 8
- Air is also being drawn into the intake plenum 221 by the intake fan 225, which air flow is forced upwardly through the riser tubes 227 located in the cooling chamber.
- the riser tubes pass though the cold water sump and also contact the evaporative media in the cooling chamber, so that the outside of the tubes are cooled.
- the air within the tubes 227 is cooled by conduction through the tubes. This relatively drier air can be directed through a suitable duct to the interior of the structure to be cooled and can be combined with the cooled air from the cooling chamber, if desired.
- air is being cooled using two simultaneous processes. Air is cooled by direct contact with water in the evaporative cooling chamber 217, raising the absolute humidity of the air cooled in this manner. Additional air is also being cooled by conductive heat transfer within the riser tubes 227. The absolute humidity of this additional air is either unchanged or only slightly changed, or decreases slightly, due to condensation on the inside of the risertubes. If desired, the two airflows can be combined into a single discharge duct as described with respect to the first embodiment of the invention, so that the discharged air consists of a mixture of relatively humid air from the evaporative process and air with near ambient humidity.
- the cold water sump (illustrated generally at 219 in Fig. 9) at the bottom of the cooling chamber serves as a cooling mass, as well as a sump.
- the water in the sump is refrigerated to near freezing by means of a commercially available, low temperature compressor similar to that used on an ice machine and which can be AC or DC operated, but is preferably operable on 12 Volt DC power.
- the compressor 209 is battery operated.
- an associated inverter 243 (in Fig. 11 ) , which in this case is located within the exhaust plenum area 215 allows the unit to be operated off AC current to, for example, charge the batteries, during non-peak hours of operation. Locating the inverter within the chilled exhaust plenum compartment prolongs its life since the operating temperature is reduced.
- the electric fans used in the intake plenum and on the cooling chamber are also preferably 12 Volt DC fans which can be driven by solar cells or storage batteries.
- Fig.'s 10, 11 and 16, 16A and 16B illustrate a particularly preferred refrigeration manifold 245 which is cooled by the compressor 209 and associated condenser 210 using traditional mechanical refrigeration techniques. While a number of different traditional manifold or coil arrangements could be utilized with the compressor 209 to cool the water in the sump 219, the preferred manifold 245 is especially efficient for the intended application. As best seen in the isolated view of Fig. 16, the manifold 245 is a "double shock" manifold having a front layer 247 and a rear layer 249. The front and rear layers or coils are spaced apart by means of a plurality of cylindrical spacers 251.
- the cylindrical spacers 251 are less wide than the total width of the manifold, leaving a distance "d" between adjacent spacers.
- the cylindrical spacers are also hollow and open at both ends, allowing water in the sump 219 to flow around and through the spacers.
- the manifold 245 is arranged in a generally horizontal plane when in place in the sump region of the cooling chamber.
- Refrigerant is supplied to and returned from the manifold layers by a pair of "splits", shown generally at 253 and 255 in Fig. 16.
- the top layer of coils is made up of loops 252, 254, 256, 258, 260, 262, 264, and 266.
- the loops are shown as broken-away halves for ease of illustration.
- the rear layer of coils is made up of loops 268, 270, 272, 274, 276, 278, 280 and 282.
- the loop halves 252-266 form a continuous coil on the front of the manifold.
- the loop halves 268-282 similarly from a continuous loop on the rear of the manifold.
- the points at which the front and rear loops exit or terminate are connected by cross-over pipes 284, 286.
- the cross-over pipes 284, 286 intersect the first loop halves (252, 282,in Figure 16B) to form the "splits 253, 255.
- the cross-over piping arrangement and the splits 253 and 255 result in a type of "interlayered flow" through the manifold. For example, refrigerant passing through the split 253 flows through branch 253B (Fig. 16) to the front layer 247 and through branch 253A to the rear layer 249. Refrigerant returning from the front and rear layers 247, 249 meets at the split 255.
- the double shock manifold with its split flow operation nearly doubles the cooling capacity of the compressor 209.
- the following description is taken from an actual test run of the device illustrated in Fig.'s 8-16B, as described above. Without intending to be limiting, the following test results are intended to illustrate the features of a particularly preferred embodiment of the invention.
- the case or housing sections of the device were formed of stainless steel.
- Two 12 volt fans, installed on opposite sides of the unit were used to draw outdoor atmospheric air into the main wet chamber, referred to herein as the "wet side" of the unit. Copper tubes extended through the wet chamber and a single 12 volt fan was used to force air through the tubes on what will be referred to as the "dry side" of the unit.
- the air supply to the dry side came through a duct that extended into the conditioned space.
- the two airstreams (dry and wet side) were combined inside the unit and directed to a single outlet.
- the unit incorporated an integral mechanical refrigeration unit used to chill the water in the sump of the wet chamber. Batteries for 12 volt DC operation of the unit and an invertor were present to allow the operation of the unit from 120 volt AC and for charging of the batteries.
- Th ⁇ test unit was set up outside an enclosed automotive repair garage in Banning, California.
- the air supply for the secondary (wet) side of the unit was taken from the outdoor atmosphere.
- the garage was approximately 30' by 35' with an approximate 14' high ceiling.
- the combined outlet airstream and the supply air to the primary (dry) sides of the unit were ducted through a door into the enclosed garage space. Both ducts were approximately 10' long and straight with no turns.
- the duct for the combined air outlet of the unit was 10.25" I. D. (inside diameter) and the duct for the primary (dry) side was 7.0" LD.
- Test # 1 For this test the unit was not plugged into AC power and ran off battery power.
- Test #2 For this test, the unit was plugged into AC power and was run off of the invertor. Outdoor ambient [also secondary (wet) inlet] 79.7 0 F, 17% RH, 532 cfm (Ft 3 /Min)
- Test # 3 Same as test #2 except the unit was moved 10' from door as described above.
- Fig. 19 shows an additional refrigeration manifold (evaporator) 260 which can be mounted within the wet chamber (217 in Fig. 9) in front of the discharge outlet 262 from the wet chamber.
- the additional refrigeration manifold 260 can be supplied with refrigerant from the existing mechanical refrigeration system which is used to cool the sump water in the wet chamber and which has been previously described.
- Fig. 19 is a simplified, schematic illustration of the existing compressor 264 and condenser 266 used to supply refrigerant between a high side 268 and a low side 270 of the double shock manifold 245 which resides in the sump region of the wet chamber 217.
- a conventional dryer 272 and an expansion device 274 are located in the path of the circulating refrigerant, in conventional fashion.
- the expansion device 274 may be a traditional expansion valve of the type known in the industry, or may be another convenient type of expansion device which provides a transition from high pressure vapor to low pressure vapor across the coils of the double shock manifold 245 to provide the cooling effect.
- the compressor 264 is fitted with a high side line 276 and low side line 278 which supply refrigerant through an expansion device 280 to the evaporative coils 282 of the additional manifold.
- a commercially available flow control valve 284 controls the return of refrigerant from the low sides, 270 and 278, respectively, of both the double shock manifold 245 and the additional refrigeration manifold 260 to the compressor 264.
- the refrigeration circuit also includes 12 Volt pump down valves 288, 291 which control the supply of refrigerant to the high sides, 268 and 276, respectively, of the manifolds.
- the pump down valves 288, 291 are wired in the same electrical circuit as the fans 231 , 233 on the sides of the wet chamber 217 so that refrigerant is only supplied to the additional manifold when the fans 231 , 233 are running.
- the compressor 264 is equipped with its own thermostat which is set to keep the sump water 219 at or about 35 degrees F. With the fans blowing and with refrigerant being circulated to the additional manifold 260, air at, for example, about 45 degrees F.
- Fig. 20 illustrates an air conditioning unit of the invention 301 installed within a structure to be cooled.
- the unit 301 has an outside duct 303 which communicates one of the fan inlets 305 on the wet chamber to the outside environment to draw in outside air.
- the oppositely arranged fan inlet 307 communicates with a duct 309 which is a part of the return air system for the room.
- the discharge outlet 311 from the wet and dry chambers (or from the wet chamber only) is ducted to the cooling vents 313 of the room. Since the unit equipped with the additional refrigeration manifold 260 condenses moisture being blown through the wet chamber 217, the condensate can be filtered for contaminants and either discharged, as at 315, or recycled in the system.
- the room can also be provide with one or more overhead automatic vents, 317, 319 which close if a door to the room is opened and which open if all of the doors to the room are closed.
- the vents then act to dump or "burp" a certain amount of basically static air from the room to the attic.
- the attic is provided with conventional exhausts 321 to release the hot air to the exterior of the structure. In this way, even without the duct 303 to the exterior of the structure, the system can be operated to move some static air out of the structure. This is in contrast to a typical evaporative unit which is nearly 100% static or to the traditional air conditioning system which may be circulating only 1 % static air.
- Fig. 21 illustrates an additional means for controlling the inlet air to the unit in order to further adjust the outlet temperature/humidity.
- the fan inlet 305 to the wet chamber is provided with a duct 323 which communicates with the bottom chamber (intake plenum) 221 of the device.
- a thermostatically operated door or gate valve mechanism can be actuated to draw air from the bottom chamber 221. If air is being drawn from the chamber 221 , then a second door or gate valve 327 shuts off the air being drawn through the duct 303 from the outside. For example, if the outside air temperature was 110 degrees F., it might be desirable to close the valve 327 and only draw in room air at, for example, 80 degrees F.
- the water within sump region 219 of the cooling chamber of the device is typically at least about 10 to 15 degrees Fahrenheit cooler than the surrounding environment. This provides the opportunity to provide some cooling to objects placed in heat exchange relationship with this water. For example, small objects can be cooled without the expenditure of significant additional amounts of energy.
- Suitable containers can be placed directly in the water on the shell side, or a cabinet accessible from the outside can be built into the shell side, or a stream of water circulated through, for example, cooling coils external to the shell side, or the like.
- the water sump region of the cooling chamber can be provided with one or more pairs of auxiliary refrigeration jacks 257, 259 which can be plugged or capped if not in use.
- the auxiliary jacks comprise an inlet and outlet point for chilled water in the sump region of the device.
- the chilled water can easily be pumped to another device in the structure to be cooled, such as another heat exchanger, to provide increased cooling.
- Fig. 17 shows one such auxiliary refrigeration device 261.
- the particular device illustrated is approximately 15" wide and 24" high so that it can conveniently be located between the studs of a wall in a residential dwelling.
- Water from the sump 219 of the air conditioner 201 is sucked through conduit 263 to the intake of a fluid pump 265.
- Pump 265 discharges chilled water through conduit 267 to coil 269.
- a 12 volt DC fan 271 located behind a 12 by 12 inch coil forces air over the coil and is used to discharge cool air from the unit into the structure to be cooled.
- the fan can be identical to the cooling chamber fans 231 and 233 used on the main air conditioner unit.
- a catch pan 274 can also be provided to catch any condensation.
- the inlet and outlet water conduits 263, 275 are packaged into a "cable" arrangement (Fig. 18) having an outer sheath of, for example a suitable polyolefin.
- the cable 277 could also contain a suitable shielded DC power supply line, illustrated as 279 in Fig. 18, for powering the fan 271 and pump 265.
- the cooling system of the invention is relatively inexpensive to manufacture.
- the system achieves as much as a 30 degree or more temperature "split" between incoming and discharged air temperatures.
- the system can be operated in dry climates on DC power which can be obtained from solar panels or from wind mills.
- the inverter lets the unit be plugged into AC power during non-peak times to recharge the DC battery power source.
- the typical unit operates on less than 20 amps of AC power under even peak conditions.
- the vortex nature of the wet chamber necessarily picks up pollutants in the air such as pollen, dust and the like.
- the pollutants drop down into the sump area of the device and can be discharged, making the unit act as an air purifier in addition to an air conditioner.
- the humidity of the system can be adjusted in several different ways, depending upon the intended end application of the unit.
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- Life Sciences & Earth Sciences (AREA)
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- Geometry (AREA)
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- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
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Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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JP2007536850A JP2008516188A (en) | 2004-10-12 | 2005-10-11 | Cooling assembly |
BRPI0516091-0A BRPI0516091A (en) | 2004-10-12 | 2005-10-11 | cooling assembly |
CA002583276A CA2583276A1 (en) | 2004-10-12 | 2005-10-11 | Cooling assembly |
IL182249A IL182249A0 (en) | 2004-10-12 | 2007-03-27 | Cooling assembly |
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US10/963,188 | 2004-10-12 | ||
US10/963,188 US20050076665A1 (en) | 2002-08-23 | 2004-10-12 | Cooling assembly |
US11/219,406 US20060032258A1 (en) | 2002-08-23 | 2005-09-01 | Cooling assembly |
US11/219,406 | 2005-09-01 |
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WO2006042286A1 true WO2006042286A1 (en) | 2006-04-20 |
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JP (1) | JP2008516188A (en) |
BR (1) | BRPI0516091A (en) |
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Cited By (1)
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WO2010130965A1 (en) * | 2009-05-14 | 2010-11-18 | Kerting | Air purification device |
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FI20065798A0 (en) * | 2006-12-13 | 2006-12-13 | Steris Europe Inc | Method and apparatus for sterilization |
US20080209935A1 (en) * | 2007-03-01 | 2008-09-04 | Joseph Gamliel | Air cooling assembly |
US7743620B1 (en) * | 2007-06-12 | 2010-06-29 | Severson Ron W | Cooling system |
US7900469B2 (en) * | 2008-02-26 | 2011-03-08 | Champion Cooler Corporation | Evaporative cooler having a novel air flow pattern |
US20090211291A1 (en) * | 2008-02-26 | 2009-08-27 | Adobeair, Inc. | Evaporative cooler having a novel support structure |
ES2791424T3 (en) * | 2009-01-18 | 2020-11-04 | Lux Et Libertas B V | Cooling device |
JP5019646B2 (en) * | 2010-04-28 | 2012-09-05 | 日本サーモスタット株式会社 | Cooling water passage device in an internal combustion engine |
US9810439B2 (en) | 2011-09-02 | 2017-11-07 | Nortek Air Solutions Canada, Inc. | Energy exchange system for conditioning air in an enclosed structure |
US9816760B2 (en) | 2012-08-24 | 2017-11-14 | Nortek Air Solutions Canada, Inc. | Liquid panel assembly |
US10584884B2 (en) | 2013-03-15 | 2020-03-10 | Nortek Air Solutions Canada, Inc. | Control system and method for a liquid desiccant air delivery system |
US11092349B2 (en) | 2015-05-15 | 2021-08-17 | Nortek Air Solutions Canada, Inc. | Systems and methods for providing cooling to a heat load |
SG10201913923WA (en) | 2015-05-15 | 2020-03-30 | Nortek Air Solutions Canada Inc | Using liquid to air membrane energy exchanger for liquid cooling |
KR101691548B1 (en) * | 2015-10-22 | 2016-12-30 | 박정규 | Air conditioner |
CA3016808C (en) * | 2016-03-08 | 2024-01-23 | Nortek Air Solutions Canada, Inc. | Systems and methods for providing cooling to a heat load |
US20180100660A1 (en) * | 2016-10-11 | 2018-04-12 | Michael Anthony Aboud | Chilled Evaporative Cooler |
US11892193B2 (en) | 2017-04-18 | 2024-02-06 | Nortek Air Solutions Canada, Inc. | Desiccant enhanced evaporative cooling systems and methods |
JP2023100421A (en) * | 2022-01-06 | 2023-07-19 | 三菱電機株式会社 | Illumination device |
WO2023194560A1 (en) * | 2022-04-06 | 2023-10-12 | Van Der Hoeven Horticultural Projects B.V. | Process to reduce the temperature in a greenhouse |
NL2031517B1 (en) * | 2022-04-06 | 2023-10-25 | Van Der Hoeven Horticultural Projects B V | Process to reduce the temperature in a greenhouse |
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- 2005-09-01 US US11/219,406 patent/US20060032258A1/en not_active Abandoned
- 2005-10-11 CA CA002583276A patent/CA2583276A1/en not_active Abandoned
- 2005-10-11 WO PCT/US2005/036721 patent/WO2006042286A1/en active Search and Examination
- 2005-10-11 BR BRPI0516091-0A patent/BRPI0516091A/en not_active Application Discontinuation
- 2005-10-11 JP JP2007536850A patent/JP2008516188A/en active Pending
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---|---|---|---|---|
WO2010130965A1 (en) * | 2009-05-14 | 2010-11-18 | Kerting | Air purification device |
FR2945450A1 (en) * | 2009-05-14 | 2010-11-19 | Kerting | DEVICE FOR PURIFYING AIR. |
Also Published As
Publication number | Publication date |
---|---|
CA2583276A1 (en) | 2006-04-20 |
US20060032258A1 (en) | 2006-02-16 |
BRPI0516091A (en) | 2008-08-19 |
JP2008516188A (en) | 2008-05-15 |
WO2006042286A9 (en) | 2011-10-27 |
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